CN104828725B - Hydraulic control system and the engineering machinery with the hydraulic control system - Google Patents
Hydraulic control system and the engineering machinery with the hydraulic control system Download PDFInfo
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- CN104828725B CN104828725B CN201410432530.3A CN201410432530A CN104828725B CN 104828725 B CN104828725 B CN 104828725B CN 201410432530 A CN201410432530 A CN 201410432530A CN 104828725 B CN104828725 B CN 104828725B
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- oil
- valve
- banked direction
- oil inlet
- hydraulic
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/02—Driving gear
- B66D1/08—Driving gear incorporating fluid motors
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
- E02D3/00—Improving or preserving soil or rock, e.g. preserving permafrost soil
- E02D3/02—Improving by compacting
- E02D3/046—Improving by compacting by tamping or vibrating, e.g. with auxiliary watering of the soil
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
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- Engineering & Computer Science (AREA)
- Structural Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Soil Sciences (AREA)
- Agronomy & Crop Science (AREA)
- Environmental & Geological Engineering (AREA)
- Fluid Mechanics (AREA)
- Physics & Mathematics (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Mining & Mineral Resources (AREA)
- Paleontology (AREA)
- Civil Engineering (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention provides a kind of hydraulic control system and the engineering machinery with the hydraulic control system.Hydraulic control system includes：First main oil pump；Hoist motor and balance valve group, hoist motor and balance valve group include the first hydraulic fluid port and the second hydraulic fluid port；First banked direction control valves, first banked direction control valves includes oil inlet, the first actuator port and the second actuator port, the oil-out of first main oil pump is connected with the oil inlet of the first banked direction control valves, first actuator port of the first banked direction control valves is connected with the first hydraulic fluid port, and the second actuator port of the first banked direction control valves is connected with the second hydraulic fluid port；Slippage pump, the oil-out of slippage pump is selectively connected or disconnected by the first oil circuit with the oil inlet of the first banked direction control valves.The hydraulic control system can improve the lifting speed for the master winch that hoist motor is driven.When the hydraulic control system is applied to the engineering machinery such as dynamic compaction machinery, because the hydraulic control system that master winch is collaborated by many pumps drives, the lifting speed of master winch is added, operating efficiency is improved.
Description
Technical field
The present invention relates to engineering machinery field, more particularly, to a kind of hydraulic control system and with the hydraulic control
The engineering machinery of system.
Background technology
Dynamic compaction machinery is when carrying out ramming operation, it is necessary to which master winch lifting hammer ram, hammer ram lifting is arrived after certain height, rammed
Hammer comes off from suspension hook, compacting foundation.In terms of the workflow of strong rammer, the lifting speed of hammer ram decides operating efficiency, speed
Faster, efficiency is higher.
In the hydraulic control system of the master winch of dynamic compaction machinery of the prior art be used for drive master winch mainly by variable
Double pump drives, but during variable dual-pump driving master winch lifting, lifting speed can be relatively slow.
The content of the invention
Present invention aims at provide a kind of hydraulic control system and engineering machinery with the hydraulic control system, the liquid
Pressure control system can improve the lifting speed for the elevator that hoist motor is driven.
First aspect present invention provides a kind of hydraulic control system, including：First main oil pump；Hoist motor and balanced valve
Group, hoist motor and balance valve group include the first hydraulic fluid port and the second hydraulic fluid port；First banked direction control valves, the first banked direction control valves include oil inlet,
First actuator port and the second actuator port, the oil-out of the first main oil pump is connected with the oil inlet of the first banked direction control valves, more than first
First actuator port of road valve is connected with the first hydraulic fluid port, and the second actuator port of the first banked direction control valves is connected with the second hydraulic fluid port；Repairing
Pump, the oil-out of slippage pump is selectively connected or disconnected by the first oil circuit with the oil inlet of the first banked direction control valves.
Further, hydraulic control system also includes：Second main oil pump；Second banked direction control valves, the second banked direction control valves includes oil-feed
Mouth, the first actuator port and the second actuator port, the oil-out of the second main oil pump are connected with the oil inlet of the second banked direction control valves, and second
First actuator port of banked direction control valves is connected with the first hydraulic fluid port, and the second actuator port of the second banked direction control valves is connected with the second hydraulic fluid port.
Further, the first oil circuit includes reversal valve, and reversal valve includes oil inlet, the first oil-out and the second oil-out；
Reversal valve has the first operating position and the second operating position, in the first operating position of reversal valve, the oil inlet of reversal valve with
The first oil-out connection of reversal valve, the oil inlet of reversal valve and the second oil-out of reversal valve disconnect, the second of reversal valve
Operating position, the oil inlet of reversal valve and the first oil-out of reversal valve disconnect, the oil inlet of reversal valve and the second of reversal valve
Oil-out is connected；The oil inlet of reversal valve and the oil-out of slippage pump have state connect, the first oil-out of reversal valve and
The oil inlet connection of first banked direction control valves, the second oil-out of reversal valve is connected with fuel tank.
Further, reversal valve is solenoid directional control valve.
Further, the first oil circuit also includes relief arrangement, and relief arrangement includes oil inlet, oil-out and oil discharge outlet, unloaded
The oil inlet of lotus device and the oil-out of slippage pump are connected, and the oil-out of relief arrangement has what is connected with the oil inlet of reversal valve
State, the oil discharge outlet of relief arrangement is connected with fuel tank.
Further, relief arrangement includes：First check valve, the oil inlet of the first check valve and the oil inlet of relief arrangement
Connection, the oil-out of the first check valve and the oil-out of relief arrangement are connected；Overflow valve, overflow valve includes oil inlet, oil-out
And control port, the oil inlet connection of the oil inlet and relief arrangement of overflow valve, the oil-out of overflow valve and the row of relief arrangement
Hydraulic fluid port is connected, and the control port of overflow valve is connected with the oil-out of the first check valve.
Further, the first oil circuit also includes the second check valve, the first oil-out of reversal valve and entering for the first banked direction control valves
Hydraulic fluid port is connected by the second check valve, and the oil inlet of the second check valve and the first oil-out of reversal valve are connected, the second check valve
Oil-out be connected with the oil inlet of the first banked direction control valves.
Further, the first oil circuit also includes revolving valve, and revolving valve includes oil inlet, oil-out and oil discharge outlet；Revolving valve
With first position and the second place, in the first position of revolving valve, the oil inlet of revolving valve is connected with the oil-out of revolving valve,
The oil inlet of revolving valve and the oil discharge outlet of revolving valve disconnect, in the second place of revolving valve, the oil inlet and revolving valve of revolving valve
Oil-out disconnect, the oil inlet of revolving valve connects with the oil discharge outlet of revolving valve；Wherein, the oil inlet of revolving valve and slippage pump
Oil-out is connected, and the oil-out of revolving valve and the oil inlet of reversal valve are connected, and the oil discharge outlet of revolving valve is connected with fuel tank.
Further, revolving valve is hydraulic control revolving valve.
Further, hydraulic control system also includes pilot valve, and pilot valve includes the first actuator port and the second working oil
Mouthful；First banked direction control valves also includes first guide's hydraulic fluid port and second guide's hydraulic fluid port, first guide's hydraulic fluid port of the first banked direction control valves and guide
The first actuator port connection of valve, second guide's hydraulic fluid port of the first banked direction control valves and the second actuator port of pilot valve are connected；Second
Banked direction control valves also includes first guide's hydraulic fluid port and second guide's hydraulic fluid port, first guide's hydraulic fluid port of the second banked direction control valves and the first of pilot valve
Actuator port is connected, and second guide's hydraulic fluid port of the second banked direction control valves and the second actuator port of pilot valve are connected.
Second aspect of the present invention also provides a kind of engineering machinery, including master winch and the hydraulic pressure for controlling master winch to rotate
Control system, wherein hydraulic control system are the hydraulic control system according to any one of first aspect present invention.
Further, engineering machinery also includes the hydraulic gyration control system of slew gear and control slew gear motion,
Wherein, the control oil of hydraulic gyration control system comes from slippage pump.
According to the hydraulic control system of the present invention and the engineering machinery with the hydraulic control system, hydraulic control system is led to
Cross hydraulic oil interflow that the hydraulic oil that slippage pump is pumped out and the first main oil pump pumped out together, realize many pumps interflow, jointly
Hoist motor and the balance valve group work of master winch are driven, therefore, the hydraulic control system can improve hoist motor and be driven
Master winch lifting speed.When the hydraulic control system is applied to the engineering machinery such as dynamic compaction machinery, because master winch passes through many pumps
The hydraulic control system driving at interflow, adds the lifting speed of master winch, improves operating efficiency.
Brief description of the drawings
The accompanying drawing for constituting the part of the application is used for providing a further understanding of the present invention, schematic reality of the invention
Apply example and its illustrate to be used to explain the present invention, do not constitute inappropriate limitation of the present invention.In the accompanying drawings：
Fig. 1 is the operation principle schematic diagram of the hydraulic control system of the preferred embodiment of the present invention.
Embodiment
Describe the present invention in detail below with reference to the accompanying drawings and in conjunction with the embodiments.It should be noted that in the feelings not conflicted
Under condition, the feature in embodiment and embodiment in the application can be mutually combined.
It should be noted that term used herein above is merely to describe embodiment, and be not intended to restricted root
According to the illustrative embodiments of the present invention.As used herein, unless the context clearly indicates otherwise, otherwise singulative
Be also intended to include plural form, additionally, it should be understood that, when in this manual using belong to "comprising" and/or " bag
Include " when, it indicates existing characteristics, step, operation, device, component and/or combinations thereof.
As shown in figure 1, the hydraulic control system of the preferred embodiment of the present invention mainly include variable dual-pump 1, hoist motor and
Balance valve group 7, the first banked direction control valves 8, the second banked direction control valves 9 and slippage pump 2.Variable dual-pump 1 includes the first main oil pump 11 and the second master
Oil pump 12.Hoist motor and balance valve group 7 include the first hydraulic fluid port 7A and the second hydraulic fluid port 7B.First banked direction control valves 8 include oil inlet 8P,
First actuator port 8A and the second actuator port 8B.The oil inlet 8P of the oil-out of first main oil pump 11 and the first banked direction control valves 8 connects
It is logical.First actuator port 8A of the first banked direction control valves 8 is connected with the first hydraulic fluid port 7A.Second actuator port 8B of the first banked direction control valves 8 with
Second hydraulic fluid port 7B is connected.Second banked direction control valves 9 includes oil inlet 9P, the first actuator port 9A and the second actuator port 9B.Second master
The oil-out of oil pump 12 is connected with the oil inlet 9P of the second banked direction control valves 9.The oil of first actuator port 9A of the second banked direction control valves 9 and first
Mouth 7A connections.Second actuator port 9B of the second banked direction control valves 9 is connected with the second hydraulic fluid port 7B.The oil-out of slippage pump 2 and more than first
The oil inlet 8P of road valve 8 is selectively connected or disconnected by the first oil circuit.
The hydraulic oil that the hydraulic control system is pumped out by hydraulic oil and variable dual-pump 1 that slippage pump 2 is pumped out collaborates
Together, realize that three pumps collaborate, the hoist motor and balance valve group 7 of common driving master winch work, therefore, the hydraulic control system
System can improve the lifting speed for the master winch that hoist motor is driven.
Preferably, in the present embodiment, in order to realize the oil-out of slippage pump 2 and the oil inlet 8P of the first banked direction control valves 8
Selectively connect or disconnect, the first oil circuit includes reversal valve 4.
As shown in figure 1, reversal valve 4 includes oil inlet 4P, the first oil-out 4A and the second oil-out 4T.Reversal valve 4 has
First operating position and the second operating position.In the first operating position of reversal valve 4, oil inlet 4P and the reversal valve 4 of reversal valve 4
The first oil-out 4A connections, the oil inlet 4P of reversal valve 4 and reversal valve 4 the second oil-out 4T disconnects.The of reversal valve 4
Two operating positions, the oil inlet 4P of reversal valve 4 disconnects with the first oil-out 4A of reversal valve 4, and the oil inlet 4P of reversal valve 4 is with changing
Connected to the second oil-out 4T of valve 4.Wherein, the oil inlet 4P of reversal valve 4 has the shape connected with the oil-out of slippage pump 2
State, the first oil-out 4A of reversal valve 4 is connected with the oil inlet 8P of the first banked direction control valves 8, the second oil-out 4T and the oil of reversal valve 4
Case is connected.
The effect of reversal valve 4 is whether control hydraulic control system realizes that three pumps collaborate.When needing three pumps interflow, commutation
Valve 4 switches to the first operating position, connects the oil circuit of the banked direction control valves 8 of slippage pump 2 and first, makes slippage pump 2 and the pump of variable dual-pump three
Interflow.It is highly preferred that reversal valve 4 is solenoid directional control valve, for example can be two-bit triplet solenoid directional control valve.
As shown in figure 1, in the present embodiment, the first oil circuit also includes relief arrangement 6, relief arrangement 6 include oil inlet 6P,
Oil-out 6A and oil discharge outlet 6T, the oil inlet 6P of relief arrangement 6 is connected with the oil-out of slippage pump 2, the oil-out of relief arrangement 6
6A has the state connected with the oil inlet 4P of reversal valve 4, and the oil discharge outlet 6T of relief arrangement 6 is connected with fuel tank.
Specifically, relief arrangement 6 includes the first check valve 62 and overflow valve 61.The oil inlet of first check valve 62 and off-load
The oil inlet 6P connections of device 6, the oil-out of the first check valve 62 is connected with the oil-out 6A of relief arrangement 6.Overflow valve 61 is wrapped
Oil inlet, oil-out and control port are included, the oil inlet of overflow valve 61 is connected with the oil inlet 6P of relief arrangement 6, overflow valve 61
Oil-out be connected with the oil discharge outlet 6T of relief arrangement 6, the oil-out of the control port of overflow valve 61 and the first check valve 62 connects
Connect.
During three pump interflow work, when the operating pressure of hydraulic control system be the oil-out side of the first check valve 62 pressure it is big
When the setting value of the overflow valve 61 of relief arrangement 6, overflow valve 61 is opened, and the hydraulic oil that slippage pump 2 is pumped out passes through overflow valve 61
Fuel tank is flowed back to, slippage pump 2 is no longer participate in the work at interflow, and three pumps collaborate the Dual-pump flow-converging for being changed into variable dual-pump 1.
Additionally preferably, the first oil circuit also includes the second check valve 5.First oil-out 4A of reversal valve 4 and the first multichannel
The oil inlet 8P of valve 8 is connected by the second check valve 5, the oil inlet 5A of the second check valve 5 and the first oil-out 4A of reversal valve 4
Connection, the oil-out 5B of the second check valve 5 is connected with the oil inlet 8P of the first banked direction control valves 8.Second check valve 5 can prevent second
The hydraulic oil that main oil pump 12 is pumped out enters the oil-out of slippage pump 2, so as to protect slippage pump 2.
As shown in figure 1, in the present embodiment, the first oil circuit also includes revolving valve 3.Revolving valve 3 includes oil inlet 3P, oil-out
3C and oil discharge outlet 3T.Revolving valve 3 has first position and the second place.In first position, oil inlet 3P and the revolution of revolving valve 3
The oil-out 3C connections of valve 3, the oil inlet 3P of revolving valve 3 disconnects with the oil discharge outlet 3T of revolving valve 3.In the second place, revolving valve 3
The oil-out 3C of oil inlet 3P and revolving valve 3 disconnect, the oil inlet 3P of revolving valve 3 is connected with the oil discharge outlet 3T of revolving valve 3.Its
In, the oil inlet 3P of revolving valve 3 is connected with the oil-out of slippage pump 2, the oil-out 3C of revolving valve 3 and the oil inlet of reversal valve 4
4P connections, the oil discharge outlet 3T of revolving valve 3 is connected with fuel tank.The oil-out 3C and oil discharge outlet 3T of revolving valve 3 internal oil passages do not connect
It is logical.
The purpose of revolving valve 3 is set to be the hydraulic gyration of the slew gear for the engineering machinery where hydraulic control system
Control system provides control oil.Preferably, revolving valve 3 is hydraulic control revolving valve.The setting is beneficial to reduce equipment cost, improves equipment
Utilization rate.
As shown in figure 1, the present embodiment uses three six-way transfer valves as revolving valve 3, three six-way transfer valves have
Middle position and upper with the next two operating positions, when three six-way transfer valves are in middle position, i.e., foregoing the in revolving valve 3
One position, and three six-way valves be in it is upper and the next when, due to three six-way transfer valves in the hydraulic control system
In three oil-outs, two oil-outs are connected to fuel tank, and non-return valve by non-return valve up and down in addition to middle oil-out 3C
Installation direction to prevent hydraulic oil from flowing to fuel tank, therefore, the bar of the upper and the next second place requirement for meeting revolving valve 3
Part, it is thereby possible to select upper and the next one is used as the second place.Though in addition, not shown revolving valve 3 and hydraulic pressure in Fig. 1
The annexation of rotary control system, it is, however, preferable that the valve position by controlling revolving valve 3, can make what slippage pump 2 was pumped
Hydraulic oil is delivered to the hydraulic gyration control system by the revolving valve 3, to control the work of rotary system, it is preferable that mending
When oil pump 2 is that hydraulic gyration control system delivery hydraulic pressure is oily, stop to hoist motor and balance valve group 7 delivery hydraulic pressure oil.
Preferably, hydraulic control system also includes pilot valve 10.Pilot valve 10 includes the first actuator port 10A and the second work
Make hydraulic fluid port 10B.First banked direction control valves 8 also includes first guide's hydraulic fluid port 8a and second guide's hydraulic fluid port 8b, and the first of the first banked direction control valves 8 is first
Oil diverting port 8a is connected with the first actuator port 10a of pilot valve 10, second guide's hydraulic fluid port 8b and the pilot valve 10 of the first banked direction control valves 8
The second actuator port 10b connections.Second banked direction control valves 9 also includes first guide's hydraulic fluid port 9a and the second guide hydraulic fluid port 9b, more than second
First guide's hydraulic fluid port 9a of road valve 9 is connected with the first actuator port 10a of pilot valve 10, the second guide oil of the second banked direction control valves 9
Mouth 9b is connected with the second actuator port 10b of pilot valve 10.Wherein, first guide's hydraulic fluid port 8a of the first banked direction control valves 8 and second is first
Oil diverting port 8b controls the first actuator port 8A and the second actuator port 8B of the first banked direction control valves 8 respectively.The first of second banked direction control valves 9
Guide's hydraulic fluid port 9a and second guide's hydraulic fluid port 9b control the first actuator port 9A and the second actuator port of the second banked direction control valves 9 respectively
9B。
First banked direction control valves 8 and the second banked direction control valves 9 can be specifically three six-way transfer valves.
It should be noted that, although setting slippage pump 2 in the present embodiment on the basis of variable dual-pump 1, still, do not showing
In the embodiment gone out, in only one main oil pump or in the case of having more main oil pumps, can also using the present invention utilization
Slippage pump 2 and the thought at main oil pump many pumps interflow.Moreover, the quantity of banked direction control valves is two in the present embodiment, but implement other
In example, the quantity of banked direction control valves can be configured as needed.In the present embodiment, slippage pump 2 only passes through 8 pairs of volumes of the first banked direction control valves
Raise motor and balance valve group 7 carries out repairing, but in other embodiments, slippage pump 2 can also pass through several or whole multichannels
Valve carries out repairing to hoist motor and balance valve group 7.In addition, in the present embodiment, slippage pump 2 is preferably constant displacement pump, still
In unshowned embodiment, slippage pump 2 is it is also contemplated that using variable pump.Although moreover, illustrate only in the present embodiment
One slippage pump 2, but the quantity of slippage pump 2 can also be arranged as required to as more than 2.
In the present embodiment because the first banked direction control valves 8 receives two oil pump feeds, therefore, the latus rectum of the first banked direction control valves 8 than
The latus rectum of second banked direction control valves 9 is big.If the hydraulic oil of slippage pump 2 accesses two banked direction control valves, need to increase the latus rectum of two valves,
Certainly, two banked direction control valves are accessed and connect complicated during practical operation for preferred embodiment, are not enough facilitated.
The present invention also provides a kind of engineering machinery, and the engineering machinery includes master winch and the liquid for controlling master winch to rotate
Pressure control system, wherein, hydraulic control system is foregoing hydraulic control system.Engineering machinery for example can be dynamic compaction machinery or rise
Heavy-duty machine etc..When the hydraulic control system is applied to engineering machinery, because the hydraulic control system that master winch is collaborated by three pumps is driven
It is dynamic, the lifting speed of elevator is added, operating efficiency is improved.
Preferably, engineering machinery also includes the hydraulic gyration control system of slew gear and control slew gear motion, its
In, the control oil of hydraulic gyration control system comes from slippage pump 2.The setting makes the pump of slippage pump one dual-purpose, beneficial to reduce equipment into
This, improves utilization rate of equipment and installations.
The operation principle of above hydraulic control system is as follows：
When not needing three pumps to collaborate, reversal valve 4 must not electricity, reversal valve 4 switches to the second operating position, and reversal valve 4 enters
Hydraulic fluid port 4P is communicated with the second oil-out 4T, so that the oil inlet 4P of reversal valve 4 is connected with fuel tank.The hydraulic pressure that slippage pump 2 is pumped out
Oil enters the oil inlet 3P of revolving valve 3 by relief arrangement 6, and when the rotary system work of dynamic compaction machinery, revolving valve 3 is in second
Operating position, hydraulic oil flows back to fuel tank by the oil discharge outlet 3T of revolving valve 3, when the rotary system of dynamic compaction machinery does not work, revolution
Valve 3 is in the first operating position, and hydraulic oil enters the oil inlet 4P of reversal valve 4 by the oil-out 3C of revolving valve 3, passes through commutation
Second oil-out 4T of valve 4 flows back to fuel tank.
When needing three pumps interflow, reversal valve 4 is opened, reversal valve 4 switches to the first operating position, the oil inlet of reversal valve 4
4P is communicated with the first oil-out 4A.During due to three pump interflow work, it is mainly the Working mould of compacting foundation for dynamic compaction machinery
Formula, now the rotary system of dynamic compaction machinery be failure to actuate.The hydraulic oil that slippage pump 2 is pumped out is entered by the oil-out 3C of revolving valve 3
The oil inlet 4P of reversal valve 4, entering for the first banked direction control valves 8 is entered from the first oil-out 4A of reversal valve 4 by the second check valve 5
Hydraulic fluid port 8P.Operated pilot valve 10, the unlatching of each banked direction control valves of pilot control oil control.The hydraulic oil warp of slippage pump 2 and variable dual-pump 1
The corresponding hydraulic fluid port interflow in hoist motor and balance valve group 7 after each banked direction control valves is crossed, so that three pumps interflow driving hoist motor is realized,
Improve the lifting speed of master winch.
From the above description, it can be seen that the above embodiments of the present invention realize following technique effect：When making in dynamic compaction machinery
After hydraulic pressure control control system with the three pumps interflow of the present embodiment, when needing three pumps interflow, reversal valve is set to be in the first work
Position, operated pilot valve 10, lifts master winch, and now the first main oil pump 11, the second main oil pump 12, slippage pump 2 are pumped out
Hydraulic oil collaborates in hoist motor and the import for balancing valve group after the first banked direction control valves 8 and the second banked direction control valves 9, drives elevator
Motor operations.Behind three pumps interflow, due to there is the hydraulic oil that three pumps are provided to supply elevator motor operations, hoist motor rotating speed than
Fast during 1 fuel feeding of variable dual-pump, this adds increased the operating rate of master winch so that the lifting speed of master winch is carried
Height, shortens the time that weight rises to specified altitude assignment from ground, improves the operating efficiency of the engineering machinery such as dynamic compaction machinery.
The preferred embodiments of the present invention are the foregoing is only, are not intended to limit the invention, for the skill of this area
For art personnel, the present invention can have various modifications and variations.Within the spirit and principles of the invention, that is made any repaiies
Change, equivalent substitution, improvement etc., should be included in the scope of the protection.
Claims (11)
1. a kind of hydraulic control system, it is characterised in that including：
First main oil pump (11)；
Hoist motor and balance valve group (7), the hoist motor and balance valve group (7) include the first hydraulic fluid port (7A) and the second hydraulic fluid port
(7B)；
First banked direction control valves (8), first banked direction control valves (8) includes oil inlet (8P), the first actuator port (8A) and the second work
Hydraulic fluid port (8B), the oil-out of first main oil pump (11) is connected with the oil inlet (8P) of first banked direction control valves (8), and described
The first actuator port (8A) of one banked direction control valves (8) is connected with first hydraulic fluid port (7A), the second work of first banked direction control valves (8)
Make hydraulic fluid port (8B) to connect with second hydraulic fluid port (7B)；
Slippage pump (2), the oil-out of the slippage pump (2) and the oil inlet (8P) of first banked direction control valves (8) pass through the first oil
Road selectively connects or disconnected；
Second main oil pump (12)；
Second banked direction control valves (9), second banked direction control valves (9) includes oil inlet (9P), the first actuator port (9A) and the second work
Hydraulic fluid port (9B), the oil-out of second main oil pump (12) is connected with the oil inlet (9P) of second banked direction control valves (9), and described
The first actuator port (9A) of two banked direction control valves (9) is connected with first hydraulic fluid port (7A), the second work of second banked direction control valves (9)
Make hydraulic fluid port (9B) to connect with second hydraulic fluid port (7B).
2. hydraulic control system according to claim 1, it is characterised in that first oil circuit includes reversal valve (4), institute
Stating reversal valve (4) includes oil inlet (4P), the first oil-out (4A) and the second oil-out (4T)；The reversal valve (4) has the
One operating position and the second operating position, in the first operating position of the reversal valve (4), the oil inlet of the reversal valve (4)
(4P) is connected with the first oil-out (4A) of the reversal valve (4), oil inlet (4P) and the reversal valve of the reversal valve (4)
(4) the second oil-out (4T) disconnects, in the second operating position of the reversal valve (4), the oil inlet of the reversal valve (4)
(4P) and the reversal valve (4) the first oil-out (4A) disconnect, oil inlet (4P) and the reversal valve of the reversal valve (4)
(4) the second oil-out (4T) connection；The oil-out of the oil inlet (4P) and the slippage pump (2) of the reversal valve (4) has
The state of connection, the first oil-out (4A) of the reversal valve (4) is connected with the oil inlet (8P) of first banked direction control valves (8),
The second oil-out (4T) of the reversal valve (4) is connected with fuel tank.
3. hydraulic control system according to claim 2, it is characterised in that the reversal valve (4) is solenoid directional control valve.
4. hydraulic control system according to claim 2, it is characterised in that first oil circuit also includes relief arrangement
(6), the relief arrangement (6) includes oil inlet (6P), oil-out (6A) and oil discharge outlet (6T), and relief arrangement (6) are entered
Hydraulic fluid port (6P) is connected with the oil-out of the slippage pump (2), oil-out (6A) and the reversal valve of the relief arrangement (6)
(4) oil inlet (4P) has the state of connection, and the oil discharge outlet (6T) of the relief arrangement (6) is connected with fuel tank.
5. hydraulic control system according to claim 4, it is characterised in that the relief arrangement (6) includes：
First check valve (62), the oil inlet of first check valve (62) connects with the oil inlet (6P) of the relief arrangement (6)
Connect, the oil-out of first check valve (62) is connected with the oil-out (6A) of the relief arrangement (6)；
Overflow valve (61), the overflow valve (61) includes oil inlet, oil-out and control port, the oil-feed of the overflow valve (61)
Mouth is connected with the oil inlet (6P) of the relief arrangement (6), oil-out and the relief arrangement (6) of the overflow valve (61)
Oil discharge outlet (6T) is connected, and the control port of the overflow valve (61) is connected with the oil-out of first check valve (62).
6. hydraulic control system according to claim 2, it is characterised in that first oil circuit also includes the second check valve
(5), the first oil-out (4A) of the reversal valve (4) and the oil inlet (8P) of first banked direction control valves (8) pass through described second
Check valve (5) is connected, and the oil inlet (5A) of second check valve (5) connects with the first oil-out (4A) of the reversal valve (4)
Connect, the oil-out (5B) of second check valve (5) is connected with the oil inlet (8P) of first banked direction control valves (8).
7. hydraulic control system according to claim 2, it is characterised in that first oil circuit also includes revolving valve (3),
The revolving valve (3) includes oil inlet (3P), oil-out (3C) and oil discharge outlet (3T)；The revolving valve (3) has first position
And the second place, the first position in the revolving valve (3), oil inlet (3P) and the revolving valve (3) of the revolving valve (3)
Oil-out (3C) connection, the oil discharge outlet (3T) of the oil inlet (3P) of the revolving valve (3) and the revolving valve (3) disconnects,
The second place of the revolving valve (3), the oil inlet (3P) of the revolving valve (3) and the oil-out (3C) of the revolving valve (3)
Disconnect, the oil inlet (3P) of the revolving valve (3) is connected with the oil discharge outlet (3T) of the revolving valve (3)；Wherein, the revolving valve
(3) oil inlet (3P) is connected with the oil-out of the slippage pump (2), and the oil-out (3C) of the revolving valve (3) is changed with described
Connected to the oil inlet (4P) of valve (4), the oil discharge outlet (3T) of the revolving valve (3) is connected with fuel tank.
8. hydraulic control system according to claim 7, it is characterised in that the revolving valve (3) is hydraulic control revolving valve.
9. hydraulic control system according to claim 1, it is characterised in that
The hydraulic control system also includes pilot valve (10), and the pilot valve (10) includes the first actuator port (10A) and the
Two actuator ports (10B)；
First banked direction control valves (8) also includes first guide's hydraulic fluid port (8a) and second guide's hydraulic fluid port (8b), first banked direction control valves
(8) first guide's hydraulic fluid port (8a) is connected with the first actuator port (10a) of the pilot valve (10), first banked direction control valves
(8) second guide's hydraulic fluid port (8b) is connected with the second actuator port (10b) of the pilot valve (10)；
Second banked direction control valves (9) also includes first guide's hydraulic fluid port (9a) and second guide's hydraulic fluid port (9b), second banked direction control valves
(9) first guide's hydraulic fluid port (9a) is connected with the first actuator port (10a) of the pilot valve (10), second banked direction control valves
(9) second guide's hydraulic fluid port (9b) is connected with the second actuator port (10b) of the pilot valve (10).
10. a kind of engineering machinery, including master winch and the hydraulic control system for controlling the master winch to rotate, its feature exist
In the hydraulic control system is the hydraulic control system according to any one of claim 1 to 9.
11. engineering machinery according to claim 10, it is characterised in that the engineering machinery also includes slew gear and control
The hydraulic gyration control system of the slew gear motion is made, wherein, the control oil of the hydraulic gyration control system comes from institute
State slippage pump (2).
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| CN106192977A (en) * | 2016-07-18 | 2016-12-07 | 华中科技大学 | A kind of hydraulic hybrid dynamic compaction machinery |
| CN108944432A (en) * | 2018-06-29 | 2018-12-07 | 山推工程机械股份有限公司 | A kind of travelling system of spreader and paver |
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| CN104828725A (en) | 2015-08-12 |
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Effective date of registration: 20200927 Address after: No.202 Xuanfu street, Xuanhua District, Zhangjiakou, Hebei Province Patentee after: Hebei Leisa Heavy Construction Machinery Co., Ltd Address before: 102206 Beijing, Shahe, Changping District Town, Sha Yang Road, Beiqi Futian Motor Company Limited law and Intellectual Property Department Patentee before: BEIQI FOTON MOTOR Co.,Ltd. |
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